JP2020056486A - Disc brake - Google Patents

Disc brake Download PDF

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Publication number
JP2020056486A
JP2020056486A JP2018189270A JP2018189270A JP2020056486A JP 2020056486 A JP2020056486 A JP 2020056486A JP 2018189270 A JP2018189270 A JP 2018189270A JP 2018189270 A JP2018189270 A JP 2018189270A JP 2020056486 A JP2020056486 A JP 2020056486A
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Japan
Prior art keywords
rotor
housing
pressing
disc brake
holes
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Withdrawn
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JP2018189270A
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Japanese (ja)
Inventor
智宏 横山
Tomohiro Yokoyama
智宏 横山
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Toyota Motor Corp
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Toyota Motor Corp
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Priority to JP2018189270A priority Critical patent/JP2020056486A/en
Priority to CN201910890816.9A priority patent/CN111005954A/en
Priority to US16/591,690 priority patent/US20200109751A1/en
Publication of JP2020056486A publication Critical patent/JP2020056486A/en
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
    • F16D55/2265—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
    • F16D55/227—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing by two or more pins
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T1/00—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles
    • B60T1/02—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels
    • B60T1/06—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels
    • B60T1/065—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels employing disc
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
    • F16D55/2265—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/0006—Noise or vibration control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/005—Components of axially engaging brakes not otherwise provided for
    • F16D65/0056—Brake supports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • F16D65/183—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes with force-transmitting members arranged side by side acting on a spot type force-applying member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0008—Brake supports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0016—Brake calipers
    • F16D2055/002—Brake calipers assembled from a plurality of parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0075—Constructional features of axially engaged brakes
    • F16D2055/0091—Plural actuators arranged side by side on the same side of the rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/02—Fluid pressure
    • F16D2121/04—Fluid pressure acting on a piston-type actuator, e.g. for liquid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/02—Fluid-pressure mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/02—Fluid-pressure mechanisms
    • F16D2125/04—Cylinders

Abstract

To improve a disc brake, in which a pressing device includes a first pressing member and a second pressing member, to enable output of a large brake force.SOLUTION: A disc brake is provided with multiple first pressing members 36. Since an inner pad 4 is pressed to a rotor 3 by each of the first pressing members, a contact area between the inner pad and the rotor can be increased and a surface pressure can be uniformized. As a result, a frictional force acting among the inner pad, an outer pad 6, and the rotor can be increased to increase a brake force applied to a wheel.SELECTED DRAWING: Figure 2

Description

本発明は、車両の車輪に搭載されたディスクブレーキに関するものである。   The present invention relates to a disc brake mounted on a vehicle wheel.

特許文献１には、(a)車輪とともに回転するロータを挟んで位置するインナパッドおよびアウタパッドと、(b)インナパッドおよびアウタパッドをロータに押し付ける押付装置と、(c)非回転体に取り付けられ、押付装置を保持するハウジングとを含む浮動式のディスクブレーキが記載されている。また、押付装置は、(i)ハウジングに保持され、ロータに向かって移動可能な１つの第１押圧部材およびロータから離れる向きに移動可能な１つの第２押圧部材と、(ii)ハウジングに、ロータの回転軸線と平行な方向に相対移動可能に保持され、第２押圧部材の移動に伴って移動し、アウタパッドをロータに押し付けるキャリパとを含む。キャリパは、インナパッドおよびアウタパッドを、外周面において跨ぐ形状を成す。   Patent Literature 1 discloses (a) an inner pad and an outer pad which are positioned with a rotor that rotates with wheels interposed therebetween, (b) a pressing device for pressing the inner pad and the outer pad against the rotor, and (c) a non-rotating body, A floating disc brake is described that includes a housing for holding the pressing device. Further, the pressing device includes (i) one first pressing member that is held by the housing and is movable toward the rotor and one second pressing member that is movable in a direction away from the rotor, and (ii) the housing includes: A caliper that is held so as to be relatively movable in a direction parallel to the rotation axis of the rotor, moves with the movement of the second pressing member, and presses the outer pad against the rotor. The caliper has a shape that straddles the inner pad and the outer pad on the outer peripheral surface.

特開２０１７−２０７１０４号公報JP 2017-207104 A

本発明の課題は、第１押圧部材と第２押圧部材とを備えたディスクブレーキの改良であり、大きな制動力を出力可能とすることである。   An object of the present invention is to improve a disc brake including a first pressing member and a second pressing member, and to output a large braking force.

本発明に係るディスクブレーキにおいては、第１押圧部材が複数設けられる。複数の第１押圧部材の各々によりインナパッドがロータに押し付けられるため、インナパッドとロータとの接触面積を広くしたり、面圧の均一化を図ったりすることができる。その結果、インナパッド、アウタパッドとロータとの間に作用する摩擦力を大きくすることができ、車輪に加えられる制動力を大きくすることができる。   In the disc brake according to the present invention, a plurality of first pressing members are provided. Since the inner pad is pressed against the rotor by each of the plurality of first pressing members, the contact area between the inner pad and the rotor can be increased, and the surface pressure can be made uniform. As a result, the frictional force acting between the inner pad, the outer pad, and the rotor can be increased, and the braking force applied to the wheels can be increased.

本発明の実施例１に係るディスクブレーキの斜視図である。1 is a perspective view of a disc brake according to Embodiment 1 of the present invention. 図７のIII-III断面図である。FIG. 8 is a sectional view taken along the line III-III of FIG. 7. 図７のI-I断面図である。It is II sectional drawing of FIG. 図７のII-II断面図である。FIG. 8 is a sectional view taken along the line II-II of FIG. 7. 上記ディスクブレーキの平面図である。FIG. 3 is a plan view of the disc brake. 上記ディスクブレーキの構成要素であるフレームの斜視図である。FIG. 2 is a perspective view of a frame that is a component of the disc brake. 上記ディスクブレーキの軸線と直交する向きの断面図である。It is sectional drawing of the direction orthogonal to the axis line of the said disc brake. 上記ディスクブレーキの正面図である。It is a front view of the above-mentioned disc brake. 上記ディスクブレーキの作動を概念的に示す図である。It is a figure which shows notionally the operation of the said disc brake. 上記ディスクブレーキの作動を概念的に示す図（側面図）である。It is a figure (side view) which shows operation of the above-mentioned disk brake notionally.

発明の実施形態Embodiment of the Invention

以下、本発明の一実施形態である、車両の車輪に設けられたディスクブレーキについて図面に基づいて説明する。   Hereinafter, a disc brake provided on a wheel of a vehicle, which is an embodiment of the present invention, will be described with reference to the drawings.

本実施例に係るディスクブレーキは、液圧により作動させられる浮動型のディスクブレーキである。
本ディスクブレーキは、図１〜４に示すように、(I)車輪と共に回転させられるロータ３と、(II)ロータ３の両側に位置するインナパッド４およびアウタパッド６と、(III)押付装置８と、(III)押付装置８を保持するハウジング１０とを含む。押付装置８は、複数のホイールシリンダ１４ａ等とフレーム１６とを含む。また、図３に示すように、ロータ３の回転軸線Ｌと押付装置８の中心軸線Ｍとは平行である。そのため、ロータ３の回転軸線Ｌと平行な方向、押付装置８の中心軸線Ｍと平行な方向を、単に軸線方向と称する場合がある。また、軸線方向において、アウタパッド６が位置する側が車両の外側であり、インナパッド４が位置する側が車両の内側である。 The disc brake according to the present embodiment is a floating disc brake that is operated by hydraulic pressure.
As shown in FIGS. 1 to 4, the disc brake includes (I) a rotor 3 rotated together with wheels, (II) an inner pad 4 and an outer pad 6 located on both sides of the rotor 3, and (III) a pressing device 8 And (III) a housing 10 for holding the pressing device 8. The pressing device 8 includes a plurality of wheel cylinders 14 a and the like and a frame 16. Further, as shown in FIG. 3, the rotation axis L of the rotor 3 and the center axis M of the pressing device 8 are parallel. Therefore, a direction parallel to the rotation axis L of the rotor 3 and a direction parallel to the central axis M of the pressing device 8 may be simply referred to as an axial direction. In the axial direction, the side where the outer pad 6 is located is the outside of the vehicle, and the side where the inner pad 4 is located is the inside of the vehicle.

ハウジング１０は、図５に示すように、(a)ロータ３より車両の内側の位置する主ハウジング部２０、(b)主ハウジング部２０からロータ３を越えて車両の外側に伸び出したブリッジ部２２、(c)ロータ３の周方向（以下、単に周方向と略称する場合がある）に隔てて設けられた一対のパッドピン２３，２４等を含む。
主ハウジング部２０は、概して、軸線方向に伸びたものであり、図２に示すように、主ハウジング部２０の内部に軸線方向に貫通する貫通孔２１が形成される。貫通孔２１は、ロータ３に近い側に開口する２つの第１穴部としての第１シリンダボア３０，３１と、ロータ３から遠い側に開口する１つの第２穴部としての第２シリンダボア３２とを含む。第１シリンダボア３０，３１は、それぞれの中心線Ｐ，Ｑが、互いに周方向に離間し、かつ、中心軸線Ｍの両側に位置して形成される。また、第１シリンダボア３０，３１には、それぞれ、第１押圧部材としての第１ピストン３６，３７がピストンシールを介して液密かつ摺動可能に嵌合される。第２シリンダボア３２は、平面視において、第２シリンダボア３２の中心軸線Ｒと押付装置８（主ハウジング部２０）の中心軸線Ｍとが一致する位置に形成され、第２押圧部材としての第２ピストン３８がピストンシールを介して液密かつ摺動可能に嵌合される。第１シリンダボア３０，３１と第２シリンダボア３２とは互いに連通していて、貫通孔２１の第１ピストン３６，３７と第２ピストン３８との間が液圧室４２とされる。第１ピストン３６，３７、第２ピストン３８は、各々、中空の有底円筒状を成し、底面である受圧面が液圧室４２に対向する姿勢で配設される。 As shown in FIG. 5, the housing 10 includes (a) a main housing portion 20 located inside the vehicle from the rotor 3, and (b) a bridge portion extending from the main housing portion 20 beyond the rotor 3 to the outside of the vehicle. 22, (c) a pair of pad pins 23, 24, etc., provided in the circumferential direction of the rotor 3 (hereinafter, may be simply referred to as circumferential direction).
The main housing portion 20 generally extends in the axial direction, and as shown in FIG. 2, a through hole 21 penetrating in the axial direction is formed inside the main housing portion 20. The through-holes 21 include first cylinder bores 30 and 31 as two first holes that open on the side closer to the rotor 3, and a second cylinder bore 32 as one second hole that opens on the side farther from the rotor 3. including. The first cylinder bores 30 and 31 are formed such that their respective center lines P and Q are circumferentially separated from each other and located on both sides of the center axis M. In addition, first pistons 36 and 37 as first pressing members are fitted to the first cylinder bores 30 and 31 via a piston seal so as to be liquid-tight and slidable, respectively. The second cylinder bore 32 is formed at a position where the center axis R of the second cylinder bore 32 coincides with the center axis M of the pressing device 8 (main housing portion 20) in a plan view, and a second piston as a second pressing member is formed. 38 is fitted in a liquid-tight and slidable manner via a piston seal. The first cylinder bores 30 and 31 and the second cylinder bore 32 communicate with each other, and a portion between the first pistons 36 and 37 and the second piston 38 of the through hole 21 is a hydraulic chamber 42. The first pistons 36 and 37 and the second piston 38 each have a hollow cylindrical shape with a bottom, and are disposed in such a manner that a pressure receiving surface as a bottom surface faces the hydraulic chamber 42.

本実施例においては、図２に示すように、主ハウジング部２０の第１シリンダボア３０，３１がそれぞれ形成された部分が第１シリンダ本体３０ｈ、３１ｈとされ、第１シリンダ本体３０ｈおよび第１ピストン３６等により第１ホイールシリンダ１４ａが構成され、第１シリンダ本体３１ｈおよび第１ピストン３７等により第１ホイールシリンダ１４ｂが構成される。また、主ハウジング部２０の第２シリンダボア３２が形成された部分が第２シリンダ本体３２ｈとされ、第２シリンダ本体３２ｈ、第２ピストン３８等により、第２ホイールシリンダ１４ｃが構成される。これら第１ホイールシリンダ１４ａ，１４ｂ、第２ホイールシリンダ１４ｃにおいて、液圧室４２は共通とされる。
それに対して、主ハウジング部２０の貫通孔２１が形成された部分、または、主ハウジング部２０がシリンダ本体とされ、シリンダ本体、第１ピストン３６，３７、第２ピストン３８等により１つのホイールシリンダが構成されると考えることもできる。 In the present embodiment, as shown in FIG. 2, the portions of the main housing portion 20 where the first cylinder bores 30, 31 are respectively formed are first cylinder bodies 30h, 31h, and the first cylinder body 30h and the first piston The first wheel cylinder 14a is constituted by 36 and the like, and the first wheel cylinder 14b is constituted by the first cylinder body 31h and the first piston 37 and the like. The portion of the main housing portion 20 where the second cylinder bore 32 is formed is a second cylinder main body 32h, and the second cylinder main body 32h, the second piston 38, and the like constitute the second wheel cylinder 14c. The hydraulic chamber 42 is common to the first wheel cylinders 14a and 14b and the second wheel cylinder 14c.
On the other hand, a portion of the main housing portion 20 where the through hole 21 is formed, or the main housing portion 20 is a cylinder main body, and one wheel cylinder is formed by the cylinder main body, the first pistons 36 and 37, the second piston 38, and the like. Can be considered to be composed.

本実施例においては、２つの第１シリンダボア３０，３１のうち、車両の前進走行中のロータ３の回転方向(図２等において前進回転方向と記載した)に対してリーディング側(回転方向の先行側)の第１シリンダボア３１の内径ｄ２がトレーリング側(回転方向の後方側)の第１シリンダボア３０の内径ｄ１より小さくされる（ｄ２＜ｄ１）。また、それに伴って第１ピストン３７の外径ｄ２が第１ピストン３６の外径ｄ１より小さくされる。すなわち、第１ピストン３７の液圧室４２に対向する受圧面の面積である受圧面積Ｓ２が第１ピストン３６の液圧室４２に対向する受圧面積Ｓ１より小さくされるのである（Ｓ２＜Ｓ１）。   In this embodiment, of the two first cylinder bores 30 and 31, the leading side (the leading rotational direction in the rotational direction) of the rotor 3 during the forward traveling of the vehicle (described as the forward rotational direction in FIG. 2 and the like). The inner diameter d2 of the first cylinder bore 31 is smaller than the inner diameter d1 of the first cylinder bore 30 on the trailing side (rear side in the rotational direction) (d2 <d1). Accordingly, the outer diameter d2 of the first piston 37 is made smaller than the outer diameter d1 of the first piston 36. That is, the pressure receiving area S2, which is the area of the pressure receiving surface of the first piston 37 facing the hydraulic chamber 42, is made smaller than the pressure receiving area S1 of the first piston 36 facing the hydraulic chamber 42 (S2 <S1). .

また、第２シリンダボア３２の中心軸線Ｍと直交する断面の断面積Ｓ３が、第１シリンダボア３０，３１の中心軸線Ｍと直交する断面の断面積Ｓ１，Ｓ２の各々の合計（Ｓ１＋Ｓ２）とほぼ同じとされ、第２ピストン３８の液圧室４２に対向する受圧面の面積Ｓ３が第１ピストン３６，３７の各々の液圧室４２に対向する受圧面の各々の面積Ｓ１，Ｓ２の合計（Ｓ１＋Ｓ２）とほぼ同じとされる。
Ｓ１＋Ｓ２≒Ｓ３
そのため、液圧室４２の液圧により第２ピストン３８に加えられる押付力と、第１ピストン３６，３７に加えられる押付力の合計とがほぼ同じとなる。インナパッド４に加えられる軸線方向の押付力とアウタパッド６に加えられる軸線方向の押付力とをほぼ同じとすることができるのである。 The cross-sectional area S3 of the cross section orthogonal to the central axis M of the second cylinder bore 32 is substantially the same as the sum (S1 + S2) of the cross-sectional areas S1 and S2 of the cross sections orthogonal to the central axis M of the first cylinder bores 30 and 31. The area S3 of the pressure receiving surface of the second piston 38 facing the hydraulic chamber 42 is the sum of the areas S1 and S2 of the pressure receiving surfaces of the first pistons 36 and 37 facing the hydraulic chamber 42 (S1 + S2 ) And almost the same.
S1 + S2 ≒ S3
Therefore, the pressing force applied to the second piston 38 by the hydraulic pressure of the hydraulic pressure chamber 42 and the total pressing force applied to the first pistons 36 and 37 are substantially the same. The axial pressing force applied to the inner pad 4 and the axial pressing force applied to the outer pad 6 can be made substantially the same.

図７，８に示すように、主ハウジング部２０の軸線方向のロータ側の端部の、周方向の両側には、一対の被取付部４６，４７が設けられる。一対の被取付部４６，４７において非回転体であるナックル等のサスペンション部材（車体側部材と称することもできる）に固定される。   As shown in FIGS. 7 and 8, a pair of mounted parts 46 and 47 are provided on both ends in the circumferential direction of the end of the main housing part 20 on the rotor side in the axial direction. The pair of mounted portions 46 and 47 are fixed to a non-rotating suspension member such as a knuckle (also referred to as a vehicle body side member).

ブリッジ部２２は、図１，５に示すように、平面視において、概してコの字型を成す。ブリッジ部２２は、周方向に隔てて設けられ、軸線方向に伸びた一対のロッド部５０，５１と一対のロッド部５０，５１を連結する連結部５２とから構成される。図７，８に示すように、連結部５２には周方向に隔てて２つの貫通孔５３，５４が形成されるとともに、主ハウジング部２０の貫通孔５３，５４に対応する部分に貫通孔５６，５７が形成され、これら貫通孔５３，５４、貫通孔５６，５７に、一対のパッドピン２３，２４が軸線方向に伸びた姿勢で支持される。パッドピン２３，２４は、貫通穴５６，５７、インナパッド４，アウタパッド６、貫通穴５３，５４を、この順に貫通する。このように、パッドピン２３，２４によりインナパッド４、アウタパッド６が軸線方向に移動可能に保持される。なお、パッドピン２３，２４には、図示しないパッドスプリングが取り付けられ、それにより、インナパッド４、アウタパッド６のガタ等が抑制され、振動や異音の発生が抑制される。   As shown in FIGS. 1 and 5, the bridge portion 22 has a generally U-shape in plan view. The bridge portion 22 is provided at a distance in the circumferential direction, and includes a pair of rod portions 50 and 51 extending in the axial direction and a connecting portion 52 connecting the pair of rod portions 50 and 51. As shown in FIGS. 7 and 8, two through holes 53 and 54 are formed in the connecting portion 52 at a distance from each other in the circumferential direction, and a through hole 56 is formed in a portion corresponding to the through holes 53 and 54 in the main housing portion 20. , 57 are formed, and the pair of pad pins 23, 24 are supported in the through holes 53, 54 and the through holes 56, 57 in a posture extending in the axial direction. The pad pins 23 and 24 pass through the through holes 56 and 57, the inner pad 4, the outer pad 6, and the through holes 53 and 54 in this order. Thus, the inner pads 4 and the outer pads 6 are held by the pad pins 23 and 24 so as to be movable in the axial direction. Note that pad springs (not shown) are attached to the pad pins 23 and 24, whereby play of the inner pad 4 and the outer pad 6 is suppressed, and generation of vibration and abnormal noise is suppressed.

また、主ハウジング部２０の軸線方向に隔てた位置に、フレーム１６と係合可能な係合凹部が２対設けられる。図２，７に示すように、２対の係合凹部のうちの一対の第１係合凹部６３，６４は、主ハウジング部２０のロータ側の端部に設けられ、他の一対の第２係合凹部６６，６７は、ロータ３から離れた側の端部に設けられる。また、第１係合凹部６３，６４、第２係合凹部６６，６７は、互いに周方向に隔たって設けられる。
本実施例において、第１係合凹部６３および第２係合凹部６６と、第１係合凹部６４および第２係合凹部６７とは、互いに中心軸線Ｍに対して対称に設けられる。すなわち、第１係合凹部６３および第２係合凹部６６と、第１係合凹部６４および第２係合凹部６７とは、中心軸線Ｍに対して対称な形状を成し、かつ、対称な位置に設けられるのである。第１係合凹部６３，６４、第２係合凹部６６，６７は、それぞれ、軸線方向に伸び、かつ、周方向に凹んだ溝部とすることができる。 Further, two pairs of engagement recesses that can be engaged with the frame 16 are provided at positions spaced apart in the axial direction of the main housing portion 20. As shown in FIGS. 2 and 7, a pair of first engagement recesses 63 and 64 of the two pairs of engagement recesses are provided at the rotor-side end of the main housing portion 20 and the other pair of second The engagement recesses 66 and 67 are provided at an end on the side away from the rotor 3. The first engagement recesses 63 and 64 and the second engagement recesses 66 and 67 are provided to be circumferentially separated from each other.
In the present embodiment, the first engagement recess 63 and the second engagement recess 66 and the first engagement recess 64 and the second engagement recess 67 are provided symmetrically with respect to the central axis M. That is, the first engagement recess 63 and the second engagement recess 66 and the first engagement recess 64 and the second engagement recess 67 have a symmetrical shape with respect to the center axis M, and are symmetrical. It is provided at the position. The first engagement recesses 63 and 64 and the second engagement recesses 66 and 67 may be grooves extending in the axial direction and concave in the circumferential direction, respectively.

フレーム１６は、図１，２，５，６に示すように、概して枠状を成す剛体であり、主ハウジング部２０に軸線方向に相対移動可能に保持される。
フレーム１６は、(i)中心軸線Ｍと直交した方向に伸び、互いに軸線方向において隔てて設けられた第１辺部７４および第２辺部７５と、(ii)第１辺部７４および第２辺部７５に交差する方向に伸び、互いに周方向において隔てて設けられた第３辺部７７および第４辺部７８とを含む。第３辺部７７および第４辺部７８は、それぞれ、第１辺部７４と第２辺部７４とを連結する。第１辺部７４と第２辺部７５とは、軸線方向において、ロータ３に対して互いに反対側に位置する。第１辺部７４は、ロータ３より車両の内側に位置し、第２ピストン３８に対向させられる。第２辺部７５は、ロータ３より車両の外側に位置し、アウタパッド６に軸方向に一体的に移動可能に係合させられる。 As shown in FIGS. 1, 2, 5, and 6, the frame 16 is a generally frame-shaped rigid body, and is held by the main housing portion 20 so as to be relatively movable in the axial direction.
The frame 16 includes (i) a first side 74 and a second side 75 that extend in a direction orthogonal to the central axis M and are spaced apart from each other in the axial direction, and (ii) a first side 74 and a second side 74. It includes a third side 77 and a fourth side 78 extending in a direction intersecting the side 75 and provided at a distance from each other in the circumferential direction. The third side 77 and the fourth side 78 connect the first side 74 and the second side 74, respectively. The first side 74 and the second side 75 are located on opposite sides of the rotor 3 in the axial direction. The first side 74 is located inside the vehicle with respect to the rotor 3 and is opposed to the second piston 38. The second side portion 75 is located outside the vehicle from the rotor 3 and is engaged with the outer pad 6 so as to be integrally movable in the axial direction.

第３辺部７７、第４辺部７８は、それぞれ、ロータ３の車両の内側と外側とに伸びて設けられるが、図１，２，５に示すように、インナパッド４、アウタパッド６の半径方向外方を越えることなく、ロータ３を越えて設けられる。   The third side portion 77 and the fourth side portion 78 are provided so as to extend inside and outside the vehicle of the rotor 3, respectively, and as shown in FIGS. 1, 2, and 5, the radius of the inner pad 4 and the outer pad 6 is provided. It is provided beyond the rotor 3 without going outside in the direction.

また、図６に示すように、第３辺部７７、第４辺部７８の、ロータ３より車両の内側に位置する部分の互いに対向する内側面には、軸線方向に隔てて２対の係合凸部が設けられる。２対の係合凸部のうちの一対の第１係合凸部８０，８２は、他の一対の第２係合凸部８４，８６よりロータ３に近い側に位置する。本実施例において、これら第１係合凸部８０および第２係合凸部８４と、第１係合凸部８２および第２係合凸部８６とは、中心軸線Ｍに対して対称に形成される。すなわち、これら第１係合凸部８０および第２係合凸部８４と、第１係合凸部８２および第２係合凸部８６とは、中心軸線Ｍに対して互いに対称な形状を成し、かつ、フレーム１６の互いに対称な位置に設けられるのである。   As shown in FIG. 6, two pairs of engaging members are provided on inner surfaces of the third side portion 77 and the fourth side portion 78 facing each other at portions located on the inside of the vehicle with respect to the rotor 3 at an axial direction. A convex portion is provided. The pair of first engagement protrusions 80 and 82 of the two pairs of engagement protrusions are located closer to the rotor 3 than the other pair of second engagement protrusions 84 and 86. In the present embodiment, the first engaging projection 80 and the second engaging projection 84 and the first engaging projection 82 and the second engaging projection 86 are formed symmetrically with respect to the center axis M. Is done. That is, the first engagement projection 80 and the second engagement projection 84 and the first engagement projection 82 and the second engagement projection 86 have shapes symmetrical with respect to the center axis M. In addition, they are provided at symmetrical positions on the frame 16.

これら第１係合凸部８０，８２が第１係合凹部６３，６４に係合させられ、第２係合凸部８４，８６が第２係合凹部６６，６７に係合させられ、それにより、フレーム１６がハウジング１０に軸線方向に移動可能に保持される。なお、第１係合凸部８０，８２と第１係合凹部６３，６４との間、第２係合凸部８４，８６と第２係合凹部６６，６７との間には、図７に示すように、板ばねであるスプリング８８を介在させることができる。例えば、スプリングを、腐食電位が、フレーム１６の腐食電位とハウジング１０の腐食電位との中間の高さのものとした場合に、フレーム１６とハウジング１０とが直接摺接させられる場合と比較して、摺接部材同士の電位差を小さくすることができ、ハウジング１０等の腐食を抑制し得る。また、スプリングにより、フレーム１６の主ハウジング部２０に対する半径方向、周方向の相対位置ずれを抑制することができ、異音の発生や振動を抑制することができる。   The first engaging projections 80 and 82 are engaged with the first engaging recesses 63 and 64, and the second engaging projections 84 and 86 are engaged with the second engaging recesses 66 and 67. Accordingly, the frame 16 is held by the housing 10 so as to be movable in the axial direction. 7 between the first engaging projections 80 and 82 and the first engaging recesses 63 and 64, and between the second engaging projections 84 and 86 and the second engaging recesses 66 and 67. As shown in FIG. 5, a spring 88 which is a leaf spring can be interposed. For example, when the spring has an erosion potential at an intermediate height between the erosion potential of the frame 16 and the erosion potential of the housing 10, the spring is compared with a case where the frame 16 and the housing 10 are directly slid. The potential difference between the sliding members can be reduced, and the corrosion of the housing 10 and the like can be suppressed. Further, the relative displacement of the frame 16 in the radial direction and the circumferential direction with respect to the main housing portion 20 can be suppressed by the spring, and generation of abnormal noise and vibration can be suppressed.

また、フレーム１６の第１辺部７４の中央部には係合凸部９０が設けられる。係合凸部９０には、図３に示すように、弾性部材としての連結用スプリング９２が取り付けられる。連結用スプリング９２は、板バネであり、側面視において溝型に曲げられて形成される嵌合部９２ａと、湾曲部９２ｂとを有する形状を成すものであり、嵌合部９２ａにおいて係合凸部９０に半径方向において嵌合され、湾曲部９２ｂの先端部が第２ピストン３８の凹部の内周面に接する状態で取り付けられるのである。連結用スプリング９２により第２ピストン３８に対するフレーム１６の位置決めを図りつつ、第２ピストン３８とフレーム１６とを一体的に移動可能とすることができる。   An engagement projection 90 is provided at the center of the first side 74 of the frame 16. As shown in FIG. 3, a connection spring 92 as an elastic member is attached to the engagement projection 90. The connection spring 92 is a leaf spring, and has a shape having a fitting portion 92a formed by being bent into a groove shape in a side view and a curved portion 92b. It is fitted in the radial direction to the portion 90, and is attached in a state where the distal end of the curved portion 92b is in contact with the inner peripheral surface of the concave portion of the second piston 38. While positioning the frame 16 with respect to the second piston 38 by the connection spring 92, the second piston 38 and the frame 16 can be integrally movable.

さらに、フレーム１６の第３辺部７７、第４辺部７８の各々のロータ３より車両の内側の部分には、一対の加工基準９６，９７が設けられる。
加工基準９６，９７は、フレーム１６の加工の際に治具を取り付ける部分である。フレーム１６を製造する場合には、切削、研磨等の加工を施した後に塗装をするのが普通であるが、加工時に用いられるクーラントの塗装への影響が少ない場合には、塗装後に加工を行うこともできる。前者の場合には、塗装が行われない部分にマスキングをする等の作業が必要となるが、後者の場合には、マスキング等の作業は不要になるが、加工時にフレーム１６に治具を取り付ける場合の治具の取付け部である加工基準が残るという問題がある。 Further, a pair of processing standards 96 and 97 are provided in the portion of the frame 16 on the third side 77 and the fourth side 78 on the inner side of the rotor 3 with respect to the vehicle.
The processing standards 96 and 97 are parts to which a jig is attached when the frame 16 is processed. In the case of manufacturing the frame 16, it is common to apply the coating after performing processing such as cutting and polishing, but if the coolant used during processing has little effect on the coating, the coating is performed after coating. You can also. In the former case, work such as masking is required on a portion where painting is not performed. In the latter case, work such as masking is not required, but a jig is attached to the frame 16 during processing. In this case, there is a problem that a processing reference as a mounting portion of the jig remains.

そこで、本実施例においては、加工基準９６，９７を、フレーム１６の第３辺部７７、第４辺部７８のロータ３に対応する部分より、車両の内側に設けた。本実施例においては、第３辺部７７、第４辺部７８のロータ３に対応する部分に、厚みが他の部分より厚い隆起部９８，９９が設けられるが、加工基準９６，９７が、隆起部９８，９９より車両の内側の部分に設けられるのである。その結果、車両の外側（すなわち、第２辺部７５の外側面１０２側）から、加工基準９６，９７が見え難くなり、車両の外側からのディスクブレーキの見栄えが悪くなることを防止することができる。   Therefore, in the present embodiment, the processing standards 96 and 97 are provided on the inside of the vehicle from the portions corresponding to the rotor 3 of the third side 77 and the fourth side 78 of the frame 16. In the present embodiment, raised portions 98 and 99 having a greater thickness than other portions are provided in portions corresponding to the rotor 3 on the third side portion 77 and the fourth side portion 78. It is provided at a portion inside the vehicle from the raised portions 98 and 99. As a result, the processing standards 96 and 97 are hardly seen from the outside of the vehicle (that is, from the outer surface 102 side of the second side portion 75), and the appearance of the disc brake from the outside of the vehicle is prevented from being deteriorated. it can.

加工基準９６，９７は、概して、三角錐形状、または、円錐形状を成すものとすることができる。加工時には、フレーム１６の種々の位置に、種々の方向から力が加えられる。それに対して、本実施例においては、治具により、フレーム１６に種々の方向から押付力を加えることが可能となり、加工時に、フレーム１６を良好に保持することが可能となるのである。   The processing criteria 96, 97 can generally be triangular pyramidal or conical. During processing, forces are applied to various positions of the frame 16 from various directions. On the other hand, in the present embodiment, the jig allows the pressing force to be applied to the frame 16 from various directions, so that the frame 16 can be favorably held during processing.

以上のように構成されたディスクブレーキは、図９に示すように、第１ホイールシリンダ１４ａ、１４ｂ、第２ホイールシリンダ１４ｃの液圧室４２の液圧により作動させられる。液圧室４２の液圧に各々のピストンの受圧面積を掛けた力である押付力が第１ピストン３６，３７、第２ピストン３８に加えられる。第１ピストン３６，３７が矢印Ｙが示す方向に、ロータ３に向かって軸線方向に移動させられ、インナパッド４がロータ３に押し付けられる。第２ピストン３８が矢印Ｘが示す向き（ロータ３から離れる向き）に軸線方向に移動させられ、フレーム１６が矢印Ｘが示す向きに移動させられる。フレーム１６の矢印Ｘ方向への移動により、アウタパッド６がロータ３に押し付けられる。ロータ３は、インナパッド４、アウタパッド６により両側から押し付けられ、インナパッド４、アウタパッド６とロータ３とが摩擦係合させられる。ディスクブレーキが作用状態となり、車輪の回転が抑制される。   As shown in FIG. 9, the disk brake configured as described above is operated by the hydraulic pressure in the hydraulic chambers 42 of the first wheel cylinders 14a, 14b and the second wheel cylinder 14c. A pressing force, which is a force obtained by multiplying the hydraulic pressure of the hydraulic pressure chamber 42 by the pressure receiving area of each piston, is applied to the first pistons 36 and 37 and the second piston 38. The first pistons 36 and 37 are moved in the axial direction toward the rotor 3 in the direction indicated by the arrow Y, and the inner pad 4 is pressed against the rotor 3. The second piston 38 is moved in the axial direction in the direction indicated by the arrow X (the direction away from the rotor 3), and the frame 16 is moved in the direction indicated by the arrow X. The outer pad 6 is pressed against the rotor 3 by the movement of the frame 16 in the direction of the arrow X. The rotor 3 is pressed from both sides by the inner pad 4 and the outer pad 6, and the inner pad 4, the outer pad 6 and the rotor 3 are frictionally engaged. The disc brake is activated and the rotation of the wheels is suppressed.

本ディスクブレーキにおいては、周方向に並んで、２つの第１ピストン３６，３７が設けられる。その結果、インナパッド４、アウタパッド３６を周方向に伸ばすことによって大きくした場合に、インナパッド４，アウタパッド６とロータ３との接触面積を大きくすることができ、大きな制動力を付与することが可能となる。   In the present disc brake, two first pistons 36 and 37 are provided side by side in the circumferential direction. As a result, when the inner pad 4 and the outer pad 36 are enlarged by extending in the circumferential direction, the contact area between the inner pad 4, the outer pad 6 and the rotor 3 can be increased, and a large braking force can be applied. Becomes

特に、動力性能が高く、大きな制動力が要求される車両において、インナパッド４、アウタパッド６を大きくすることが考えられるが、第１ピストンが１つである場合には、インナパッド４、アウタパッド６とロータ３との接触面積を増加させることが困難となり、効果的に制動力を大きくすることが困難である。それに対して、本実施例においては、インナパッド４、アウタパッド６とロータ３との間の接触面積を大きくすることができ、大きな制動力を付与することができる。その結果、大きな制動力が要求される車両にも適用することができる。   In particular, it is conceivable to increase the size of the inner pad 4 and the outer pad 6 in a vehicle that requires high power performance and a large braking force. However, when the number of the first piston is one, the inner pad 4 and the outer pad 6 are used. It is difficult to increase the contact area between the rotor and the rotor 3, and it is difficult to effectively increase the braking force. On the other hand, in the present embodiment, the contact area between the inner pad 4, the outer pad 6, and the rotor 3 can be increased, and a large braking force can be applied. As a result, the present invention can be applied to a vehicle requiring a large braking force.

しかも、リーディング側の第１ホイールシリンダ１４ｂの方がトレーリング側の第１ホイールシリンダ１４ａよりピストンの液圧室４２に対する受圧面積が小さくされる。一方、車両の前進走行中には、連れ回りにより、リーディング側の部分においてはトレーリング側の部分におけるより、インナパッド４、アウタパッド６とロータ３との間の面圧が高くなり易い。それに対して、本実施例においては、リーディング側の第１ホイールシリンダ１４ｂにおいて、トレーリング側のホイールシリンダ１４ａよりピストンに加えられる押付力が小さくされる。その結果、インナパッド４、アウタパッド６とロータ３との間のリーディング側の部分において面圧が高くなり難くなり、インナパッド４、アウタパッド３６とロータ３との面圧の均一化を図ることができる。   Moreover, the pressure receiving area of the piston with respect to the hydraulic chamber 42 is smaller in the first wheel cylinder 14b on the leading side than in the first wheel cylinder 14a on the trailing side. On the other hand, during forward running of the vehicle, the surface pressure between the inner pad 4, the outer pad 6, and the rotor 3 is more likely to be higher in the leading-side portion than in the trailing-side portion due to entrainment. On the other hand, in the present embodiment, in the first wheel cylinder 14b on the leading side, the pressing force applied to the piston from the wheel cylinder 14a on the trailing side is reduced. As a result, the surface pressure hardly increases at the leading side portion between the inner pad 4, the outer pad 6, and the rotor 3, and the surface pressure of the inner pad 4, the outer pad 36, and the rotor 3 can be made uniform. .

このように、本実施例におけるディスクブレーキにおいて、インナパッド４、アウタパッド６とロータ３との接触面積が大きくされ、面圧の均一化が図られる。接触面積が小さく、面圧が不均一である場合に比較して、ロータ３とインナパッド４、アウタパッド６との間の摩擦係数が、押付力が大きい状態において、大きくなる。その結果、より一層、車輪に大きな制動力を付与することが可能となる。   As described above, in the disc brake of the present embodiment, the contact area between the inner pad 4, the outer pad 6, and the rotor 3 is increased, and the surface pressure is made uniform. The coefficient of friction between the rotor 3 and the inner pad 4 and the outer pad 6 increases in a state where the pressing force is large, as compared with the case where the contact area is small and the surface pressure is uneven. As a result, a greater braking force can be applied to the wheels.

また、インナパッド４、アウタパッド６とロータ３との間のリーディング側の部分において、摩擦力が大きくなり難くすることができる。その結果、ロータ３、インナパッド４、アウタパッド６の偏摩耗を抑制することができる。   Further, it is possible to make it difficult for the frictional force to increase in the leading side portion between the inner pad 4, the outer pad 6, and the rotor 3. As a result, uneven wear of the rotor 3, the inner pad 4, and the outer pad 6 can be suppressed.

さらに、第１ピストン３６，３７の液圧室４２に対する受圧面の面積の合計（Ｓ１＋Ｓ２）と第２ピストン３８の液圧室４２に対する受圧面Ｓ３とが、ほぼ同じとされている。そのため、インナパッド４に加えられる軸線方向の力とアウタパッド６に加えられる軸線方向の力とをほぼ同じにすることができる。   Further, the sum of the areas of the pressure receiving surfaces of the first pistons 36 and 37 with respect to the hydraulic chamber 42 (S1 + S2) and the pressure receiving surface S3 of the second piston 38 with respect to the hydraulic chamber 42 are substantially the same. Therefore, the axial force applied to the inner pad 4 and the axial force applied to the outer pad 6 can be made substantially the same.

また、フレーム１６には、アウタパッド６のロータ３への押付力Ｆに応じた反力Ｒが付与されるのであり、互いに反対方向に押付力Ｆと反力Ｒとが付与されることになる。そして、図１０に示すように、フレーム１６において、これら力Ｆ，Ｒの作用線が、同一平面内に位置する。そのため、ディスクブレーキ２の作動時における、フレーム１６の傾きを抑制することができ、フレーム１６の傾きに起因する押付力の低下を抑制することができる。   Further, a reaction force R corresponding to the pressing force F of the outer pad 6 against the rotor 3 is applied to the frame 16, so that the pressing force F and the reaction force R are applied in directions opposite to each other. Then, as shown in FIG. 10, in the frame 16, the lines of action of these forces F and R are located on the same plane. Therefore, the inclination of the frame 16 during the operation of the disc brake 2 can be suppressed, and a decrease in the pressing force due to the inclination of the frame 16 can be suppressed.

しかも、主ハウジング部２０において、第２シリンダボア３２が、それの中心線Ｒが押付装置８の中心軸線Ｍとほぼ一致する位置に設けられる。仮に、第２ホイールシリンダを周方向に並べて複数設けた場合において、複数の第２ピストンの移動のタイミングがずれた場合等には、フレーム１６のＸ方向への移動時に、フレーム１６が傾く恐れがある。それに対して、本実施例においては、第２ホイールシリンダ４１ｃが１つ、フレーム１６の周方向の中心部に対向して設けられるため、ディスクブレーキの作動時のフレーム１６の傾きを良好に抑制することができる。   Moreover, the second cylinder bore 32 is provided in the main housing portion 20 at a position where the center line R thereof substantially coincides with the center axis M of the pressing device 8. If a plurality of second wheel cylinders are arranged in the circumferential direction and the timing of the movement of the plurality of second pistons is shifted, the frame 16 may be inclined when the frame 16 moves in the X direction. is there. On the other hand, in the present embodiment, since one second wheel cylinder 41c is provided to face the center of the frame 16 in the circumferential direction, the inclination of the frame 16 when the disc brake is actuated is favorably suppressed. be able to.

なお、主ハウジング部２０には、第１シリンダボアを３つ以上設けることができる。その場合には、それぞれの中心線が、少なくとも周方向に隔たって設けられる。第１ホイールシリンダを３つ以上設けることにより、より一層、面圧の均一化を図り、接触面積を大きくすることができる。   The main housing section 20 can be provided with three or more first cylinder bores. In that case, the respective center lines are provided at least separated in the circumferential direction. By providing three or more first wheel cylinders, the contact pressure can be further uniformed and the contact area can be increased.

また、３つ以上の第１ホイールシリンダを設けた場合には、最もリーディング側の第１ホイールシリンダの断面積が最もトレーリング側の第１ホイールシリンダの断面積より小さくなるようしたり、３つ以上の第１ホイールシリンダにおいて、トレーリング側からリーディング側に向かって、順に、断面積が小さくなるようにしたりすること等ができる。   In the case where three or more first wheel cylinders are provided, the cross-sectional area of the first wheel cylinder closest to the leading side may be smaller than the cross-sectional area of the first wheel cylinder closest to the trailing side. In the first wheel cylinder described above, the cross-sectional area can be reduced in order from the trailing side to the leading side.

さらに、ディスクブレーキ２は液圧ディスクブレーキに限らず、電動駆動力により作動させられる電動ディスクブレーキとすることもできる等、その他、本発明は、上記実施例の他、当業者の知識に基づいて種々の変更、改良を施した種々の形態で実施することができる。   Further, the present invention is not limited to the hydraulic disc brake, but may be an electric disc brake operated by an electric driving force. In addition to the above embodiments, the present invention is based on the knowledge of those skilled in the art. The present invention can be implemented in various forms with various changes and improvements.

３:ロータ ４：インナパッド ６：アウタパッド ８：押付装置 １０：ハウジング １４ａ、１４ｂ：第１ホイールシリンダ １４ｃ：第２ホイールシリンダ １６:フレーム ２０：主ハウジング部 ２１：貫通孔 ３０，３１：第１シリンダボア ３２：第２シリンダボア ３６，３７：第１ピストン ３８：第２ピストン   3: rotor 4: inner pad 6: outer pad 8: pressing device 10: housing 14a, 14b: first wheel cylinder 14c: second wheel cylinder 16: frame 20: main housing part 21: through hole 30, 31: first cylinder bore 32: second cylinder bore 36, 37: first piston 38: second piston

特許請求可能な発明Claimable invention

（１）車輪とともに回転するロータを挟んで位置するインナパッドおよびアウタパッドと、
前記インナパッドおよび前記アウタパッドを前記ロータに押し付ける押付装置と、
非回転体に取り付けられ、前記押付装置を保持するハウジングと
を含む浮動式のディスクブレーキであって、
前記押付装置が、
前記ハウジングに保持され、前記ロータに向かって移動可能な複数の第１押圧部材および前記ロータから離れる向きに移動可能な１つ以上の第２押圧部材と、
前記ハウジングに、前記ロータの回転軸線と平行な方向である軸線方向に相対移動可能に保持され、前記第２押圧部材の移動に伴って移動し、前記アウタパッドを前記ロータに押し付けるフレームと
を含むディスクブレーキ。 (1) an inner pad and an outer pad that are located with a rotor that rotates with the wheel therebetween;
A pressing device for pressing the inner pad and the outer pad against the rotor,
A floating disc brake including a housing attached to the non-rotating body and holding the pressing device,
The pressing device,
A plurality of first pressing members held by the housing and movable toward the rotor and one or more second pressing members movable in a direction away from the rotor;
A disk which is held by the housing so as to be relatively movable in an axial direction which is a direction parallel to the rotation axis of the rotor, moves with the movement of the second pressing member, and presses the outer pad against the rotor; brake.

（２）前記ハウジングに、前記ハウジングの前記ロータに近い側の部分に開口して、前記軸線方向に伸びた状態で、各々の中心線が前記ロータの周方向に隔たって、複数の第１穴部が形成され、
前記複数の第１押圧部材の各々が、前記ハウジングの前記複数の第１穴部にそれぞれ前記軸線方向に相対移動可能に保持された(1)項に記載のディスクブレーキ。
複数の第１穴部は、ハウジングの、各々の中心線が少なくともロータの周方向に隔たった位置に形成される。例えば、複数の第１穴部は、ハウジングの、各々の中心線がロータの周方向および半径方向に隔たった位置に形成することができるのである。また、複数の第１穴部は、ハウジングに、ロータの周方向に、隙間を隔てて、並んで形成することもできる。 (2) In the housing, a plurality of first holes are formed in the housing in a state of being opened in a portion of the housing close to the rotor and extending in the axial direction such that respective center lines are separated in a circumferential direction of the rotor. Part is formed,
The disc brake according to (1), wherein each of the plurality of first pressing members is held in the plurality of first holes of the housing so as to be relatively movable in the axial direction.
The plurality of first holes are formed in the housing at positions where respective center lines are separated at least in a circumferential direction of the rotor. For example, the plurality of first holes can be formed in the housing at positions where respective center lines are separated in the circumferential direction and the radial direction of the rotor. In addition, the plurality of first holes may be formed in the housing in a circumferential direction of the rotor with a gap therebetween.

（３）前記複数の第１穴部において、トレーリング側からリーディング側に向かって、この順に、内径が小さくされ、前記複数の第１押圧部材において、トレーリング側からリーディング側に向かって、この順に、外径が小さくされた(2)項に記載のディスクブレーキ。 (3) In the plurality of first holes, the inner diameter is reduced in this order from the trailing side to the leading side, and in the plurality of first pressing members, the inner diameter is reduced from the trailing side to the leading side. Disc brake according to item (2), the outer diameter of which is reduced in order.

（４）前記複数の第１穴部のうちの最もリーディング側に位置する第１穴部の内径が最もトレーリング側に位置する第１穴部の内径より小さくされ、前記複数の第１押圧部材のうちの最もリーディング側に位置する第１押圧部材の外径が最もトレーリング側に位置する第１押圧部材の外径より小さくされた(2)項または(3)項に記載のディスクブレーキ。 (4) The inner diameter of the first hole located closest to the leading side of the plurality of first holes is smaller than the inner diameter of the first hole located closest to the trailing side, and the plurality of first pressing members are provided. The disc brake according to the above mode (2) or (3), wherein the outer diameter of the first pressing member located closest to the trailing side is smaller than the outer diameter of the first pressing member located closest to the trailing side.

（５）前記ハウジングに、前記ハウジングの前記ロータから遠い側の部分に開口して、前記軸線方向に伸びた状態で１つ以上の第２穴部が形成され、
前記１つ以上の第２押圧部材が、それぞれ、前記ハウジングの前記１つ以上の第２穴部に前記軸線方向に相対移動可能に保持された(1)項ないし(4)項のいずれか１つに記載のディスクブレーキ。 (5) in the housing, one or more second holes are formed in the housing at a portion remote from the rotor and extended in the axial direction;
The one or more items (1) to (4), wherein the one or more second pressing members are respectively held in the one or more second holes of the housing so as to be relatively movable in the axial direction. Disc brake described in one.

（６）前記１つ以上の第２穴部としての１つの第２穴部が、前記ハウジングの、前記第２穴部の中心軸線が前記押付装置の周方向の中心軸線と一致する位置に形成され、
前記１つ以上の第２押圧部材としての１つの第２押圧部材が、前記ハウジングの前記１つの第２穴部に保持された(5)項に記載のディスクブレーキ。 (6) One or more second holes as the one or more second holes are formed in the housing at a position where a center axis of the second hole coincides with a center axis in a circumferential direction of the pressing device. And
The disc brake according to (5), wherein one second pressing member as the one or more second pressing members is held in the one second hole of the housing.

（７）前記ハウジングに、前記ハウジングの前記ロータに近い側の部分に開口して、前記軸線方向に伸びた状態で、各々の中心線が前記ロータの周方向に隔たって、複数の第１穴部が形成されるとともに、前記ハウジングの前記ロータから遠い側の部分に開口して、前記軸線方向に伸びた状態で１つ以上の第２穴部が形成され、
前記複数の第１穴部と前記１つ以上の第２穴部とが互いに連通させられ、その前記複数の第１穴部と前記１つ以上の第２穴部との互いに連通させられた部分が液圧室とされ、
前記押付装置が、前記液圧室の液圧により作動させられる３つ以上のホイールシリンダを含む(1)項ないし(5)項のいずれか１つに記載のディスクブレーキ。
ディスクブレーキが液圧ディスクブレーキである場合には、複数の第１押圧部材としての第１ピストンに作用する液圧と、１つ以上の第２押圧部材としての第２ピストンに作用する液圧とは同じ高さとなる。 (7) In the housing, a plurality of first holes are opened in a state where the center lines are separated from each other in the circumferential direction of the rotor while being opened in a portion of the housing closer to the rotor and extending in the axial direction. A portion is formed, and one or more second hole portions are formed in a state of being opened in a portion of the housing remote from the rotor and extending in the axial direction,
The plurality of first holes and the one or more second holes are communicated with each other, and the plurality of first holes and the one or more second holes are communicated with each other. Is a hydraulic chamber,
The disc brake according to any one of (1) to (5), wherein the pressing device includes three or more wheel cylinders operated by the hydraulic pressure of the hydraulic chamber.
When the disc brake is a hydraulic disc brake, the hydraulic pressure acting on the first piston as a plurality of first pressing members and the hydraulic pressure acting on the second piston as one or more second pressing members are determined. Are the same height.

（８）前記３つ以上のホイールシリンダが、各々の中心線が前記ロータの周方向に隔たって設けられた２つ以上のホイールシリンダである第１ホイールシリンダを含む(7)項に記載のディスクブレーキ。
本項に記載のディスクブレーキにおいて、ハウジングの第１穴部としての第１シリンダボアが形成された部分、第１押圧部材としての第１ピストン等により第１ホイールシリンダが構成される。また、ハウジングの第２穴部としての第２シリンダボアが形成された部分、第２押圧部材としての第２ピストン等により第２ホイールシリンダが構成される。第１ホイールシリンダは、各々の中心線がロータの周方向に隔たって、インナパッドに対向して２つ以上設けられ、第２ホイールシリンダがフレームに対向して１つ以上設けられる。 (8) The disk according to (7), wherein the three or more wheel cylinders include a first wheel cylinder which is two or more wheel cylinders each provided with a center line spaced apart in a circumferential direction of the rotor. brake.
In the disc brake described in this section, a first wheel cylinder is constituted by a portion of the housing in which the first cylinder bore is formed as the first hole, the first piston as the first pressing member, and the like. A second wheel cylinder is constituted by a portion of the housing in which a second cylinder bore as a second hole is formed, a second piston as a second pressing member, and the like. Two or more first wheel cylinders are provided facing the inner pad with their respective center lines separated in the circumferential direction of the rotor, and one or more second wheel cylinders are provided facing the frame.

（９）前記１つ以上の第２押圧部材の各々の前記液圧室に対向する受圧面の面積の合計と、前記複数の第１押圧部材の各々の前記液圧室に対向する受圧面の各々の面積の合計とが同じとされた(7)項または(8)項に記載のディスクブレーキ。
１つ以上の第２押圧部材の各々の液圧室に対向する受圧面の面積の合計と、複数の第１押圧部材の各々の液圧室に対向する受圧面の面積の合計とが同じであるとは、ほぼ同じの意味であり、厳密に同じである場合に限定されない。本項に記載のディスクブレーキにおいて、１つ以上の第２押圧部材の各々に加えられる液圧と複数の第１押圧部材の各々に加えられる液圧とが同じ高さである場合には、１つ以上の第２押圧部材の各々に加えられる押付力の合計と複数の第１押圧部材の各々に加えられる押付力の合計とが同じとなる。それにより、インナパッドのロータに対する押付力と、アウタパッドのロータに対する押付力とが同じとなり、ディスクブレーキを良好に作動させることが可能となる。 (9) The sum of the areas of the pressure receiving surfaces of each of the one or more second pressing members facing the hydraulic pressure chamber, and the sum of the areas of the pressure receiving surfaces of each of the plurality of first pressing members facing the hydraulic pressure chamber. The disc brake according to the above mode (7) or (8), wherein the sum of the areas is the same.
The sum of the areas of the pressure receiving surfaces of each of the one or more second pressing members facing the hydraulic chambers is the same as the sum of the areas of the pressure receiving surfaces of each of the plurality of first pressing members facing each hydraulic chamber. The meaning of “being” has almost the same meaning, and is not limited to the case of being exactly the same. In the disc brake described in this section, when the hydraulic pressure applied to each of the one or more second pressing members and the hydraulic pressure applied to each of the plurality of first pressing members are the same, 1 The sum of the pressing forces applied to each of the one or more second pressing members is the same as the sum of the pressing forces applied to each of the plurality of first pressing members. As a result, the pressing force of the inner pad against the rotor becomes the same as the pressing force of the outer pad against the rotor, and the disc brake can be operated satisfactorily.

（１０）前記複数の第１押圧部材の各々に加えられる押付力の合計と、前記１つ以上の第２押圧部材の各々に加えられる押付力の合計とが同じとされた(1)項ないし(9)項のいずれか１つに記載のディスクブレーキ。
複数の第１押圧部材の各々に加えられる押付力の合計と１つ以上の第２押圧部材の各々に加えられる押付力の合計とが同じであるとは、ほぼ同じの意味であり、厳密に同じである場合に限定されない。 (10) The sum of the pressing forces applied to each of the plurality of first pressing members and the sum of the pressing forces applied to each of the one or more second pressing members are the same. The disc brake according to any one of the above items (9).
The fact that the sum of the pressing forces applied to each of the plurality of first pressing members and the sum of the pressing forces applied to each of the one or more second pressing members is the same means almost exactly, It is not limited to the same case.

（１１）前記フレームが、概して枠状を成し、前記第２押圧部材に対向する第１辺部と、前記アウタパッドに前記ロータの回転軸線と平行な方向に一体的に移動可能に係合させられた第２辺部と、前記第１辺部と前記第２辺部とを連結し、互いに、周方向に隔てて設けられた第３辺部、第４辺部とを含む(1)項ないし(10)項のいずれか１つに記載のディスクブレーキ。
フレームは、第３辺部、第４辺部がインナパッド、アウタパッドを外周部から跨がない姿勢で、取り付けられる。 (11) The frame is generally frame-shaped, and the first side portion facing the second pressing member and the outer pad are integrally movably engaged with the outer pad in a direction parallel to the rotation axis of the rotor. (1) includes a second side portion, a third side portion, and a fourth side portion, which connect the first side portion and the second side portion, and are provided at a distance from each other in a circumferential direction. The disc brake according to any one of the above items (10) to (10).
The frame is attached such that the third side and the fourth side do not straddle the inner pad and the outer pad from the outer peripheral portion.

（１２）前記第３辺部と前記第４辺部とが、それぞれ、ロータに対応する部分に、厚みが厚い隆起部と、前記隆起部より前記車両の内側に位置する部分に設けられた加工基準とを含む(11)項に記載のディスクブレーキ。
加工基準が隆起部より車両の内側に設けられるため、車両の外側から加工基準が見え難くなる。 (12) Processing in which the third side and the fourth side are provided in a portion corresponding to the rotor, a thick raised portion, and a portion located on the inside of the vehicle with respect to the raised portion. Disc brake according to (11), including criteria.
Since the processing reference is provided inside the vehicle from the raised portion, the processing reference becomes difficult to see from the outside of the vehicle.

（１３）前記フレームに形成された少なくとも一対の係合凸部が、前記ハウジングに形成された少なくとも一対の係合凹部に係合させられることにより、前記フレームが前記ハウジングに軸線方向に移動可能に保持される(1)項ないし(12)項のいずれか１つに記載のディスクブレーキ。 (13) At least one pair of engagement projections formed on the frame is engaged with at least one pair of engagement recesses formed on the housing, so that the frame can move in the housing in the axial direction. The disc brake according to any one of (1) to (12), which is held.

Claims (9)

車輪とともに回転するロータを挟んで位置するインナパッドおよびアウタパッドと、
前記インナパッドおよび前記アウタパッドを前記ロータに押し付ける押付装置と、
非回転体に取り付けられ、前記押付装置を保持するハウジングと
を含む浮動式のディスクブレーキであって、
前記押付装置が、
前記ハウジングに保持され、前記ロータに向かって移動可能な複数の第１押圧部材および前記ロータから離れる向きに移動可能な１つ以上の第２押圧部材と、
前記ハウジングに、前記ロータの回転軸線と平行な方向である軸線方向に相対移動可能に保持され、前記第２押圧部材の移動に伴って移動し、前記アウタパッドを前記ロータに押し付けるフレームと
を含むディスクブレーキ。 An inner pad and an outer pad which are located with the rotor rotating with the wheels therebetween,
A pressing device for pressing the inner pad and the outer pad against the rotor,
A floating disc brake including a housing attached to the non-rotating body and holding the pressing device,
The pressing device,
A plurality of first pressing members held by the housing and movable toward the rotor and one or more second pressing members movable in a direction away from the rotor;
A disk which is held by the housing so as to be relatively movable in an axial direction which is a direction parallel to the rotation axis of the rotor, moves with the movement of the second pressing member, and presses the outer pad against the rotor; brake. 前記ハウジングに、前記ハウジングの前記ロータに近い側の部分に開口して、前記軸線方向に伸びた状態で、各々の中心線が前記ロータの周方向に隔たって、複数の第１穴部が形成され、
前記複数の第１押圧部材の各々が、前記ハウジングの前記複数の第１穴部にそれぞれ前記軸線方向に相対移動可能に保持された請求項１に記載のディスクブレーキ。 A plurality of first holes are formed in the housing so that each of the center lines is spaced apart in a circumferential direction of the rotor while being opened in a portion of the housing closer to the rotor and extending in the axial direction. And
The disc brake according to claim 1, wherein each of the plurality of first pressing members is held in the plurality of first holes of the housing so as to be relatively movable in the axial direction. 前記複数の第１穴部において、トレーリング側からリーディング側に向かって、この順に、内径が小さくされ、前記複数の第１押圧部材において、トレーリング側からリーディング側に向かって、この順に、外径が小さくされた請求項２に記載のディスクブレーキ。   In the plurality of first holes, the inner diameter is reduced in this order from the trailing side to the leading side, and the outer diameter is reduced in this order in the plurality of first pressing members from the trailing side to the leading side. 3. The disc brake according to claim 2, wherein the diameter is reduced. 前記複数の第１穴部のうちの最もリーディング側に位置する第１穴部の内径が最もトレーリング側に位置する第１穴部の内径より小さくされ、前記複数の第１押圧部材のうちの最もリーディング側に位置する第１押圧部材の外径が最もトレーリング側に位置する第１押圧部材の外径より小さくされた請求項２または３に記載のディスクブレーキ。   The inner diameter of the first hole located closest to the leading side of the plurality of first holes is smaller than the inner diameter of the first hole located closest to the trailing side, and the inner diameter of the plurality of first pressing members is 4. The disc brake according to claim 2, wherein the outer diameter of the first pressing member located closest to the leading side is smaller than the outer diameter of the first pressing member located closest to the trailing side. 前記ハウジングに、前記ハウジングの前記ロータから遠い側の部分に開口して、前記軸線方向に伸びた状態で、自身の中心線が、前記押付装置の周方向の中心軸線と一致する状態で１つの第２穴部が形成され、
前記１つ以上の第２押圧部材としての１つの第２押圧部材が、前記ハウジングの前記１つの第２穴部に前記軸線方向に相対移動可能に保持された請求項１ないし４のいずれか１つに記載のディスクブレーキ。 The housing has an opening at a portion of the housing remote from the rotor and extends in the axial direction, and one center line of the housing is aligned with the circumferential center axis of the pressing device. A second hole is formed,
The one second pressing member as the one or more second pressing members is held in the one second hole of the housing so as to be relatively movable in the axial direction. Disc brake described in one. 前記ハウジングに、前記ハウジングの前記ロータに近い側の部分に開口して、前記軸線方向に伸びた状態で、各々の中心線が前記ロータの周方向に隔たって、複数の第１穴部が形成されるとともに、前記ハウジングの前記ロータから遠い側の部分に開口して、前記軸線方向に伸びた状態で、１つ以上の第２穴部が形成され、
前記複数の第１穴部と前記１つ以上の第２穴部とが互いに連通させられ、前記複数の第１穴部と前記１つ以上の第２穴部との互いに連通させられた部分が液圧室とされ、
前記押付装置が、前記液圧室の液圧により作動させられる３つ以上のホイールシリンダを含む請求項１ないし５のいずれか１つに記載のディスクブレーキ。 A plurality of first holes are formed in the housing so that each of the center lines is spaced apart in a circumferential direction of the rotor while being opened in a portion of the housing closer to the rotor and extending in the axial direction. And at least one second hole is formed in a state where the housing is open to a portion of the housing farther from the rotor and extends in the axial direction,
The plurality of first holes and the one or more second holes are communicated with each other, and the portion of the plurality of first holes and the one or more second holes is communicated with each other. Hydraulic chamber,
The disc brake according to any one of claims 1 to 5, wherein the pressing device includes three or more wheel cylinders operated by the hydraulic pressure of the hydraulic chamber. 前記３つ以上のホイールシリンダが、各々の中心線が、前記ロータの周方向に隔たって設けられた２つ以上のホイールシリンダである第１ホイールシリンダを含む請求項６に記載のディスクブレーキ。   7. The disc brake according to claim 6, wherein the three or more wheel cylinders include a first wheel cylinder whose center line is two or more wheel cylinders provided at intervals in a circumferential direction of the rotor. 前記１つ以上の第２押圧部材の各々の前記液圧室に対向する受圧面の面積の合計と、前記複数の第１押圧部材の各々の前記液圧室に対向する受圧面の面積の合計とが同じとされた請求項６または７に記載のディスクブレーキ。   The sum of the areas of the pressure receiving surfaces of each of the one or more second pressing members facing the hydraulic chamber, and the sum of the areas of the pressure receiving surfaces of each of the plurality of first pressing members facing the hydraulic chamber. The disc brake according to claim 6 or 7, wherein 前記複数の第１押圧部材各々に加えられる押付力の合計と、前記１つ以上の第２押圧部材の各々に加えられる押付力の合計とが同じとされた請求項１ないし８のいずれか１つに記載のディスクブレーキ。   9. The device according to claim 1, wherein the sum of the pressing forces applied to each of the plurality of first pressing members is the same as the sum of the pressing forces applied to each of the one or more second pressing members. 9. Disc brake described in one.
JP2018189270A 2018-10-04 2018-10-04 Disc brake Withdrawn JP2020056486A (en)

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DE112021001859T5 (en) 2020-03-26 2023-02-23 Denso Corporation DISTANCE ESTIMATION DEVICE

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